Valve for power transmissions



D. B. GARDINER VALVE FOR POWER TRANSMISSIONS April 7, 1953 2 sl-mETs-sEEw 1 Filed June 28, 1945 INVENTOR. DUNCAN B. GARDINER 5 w 1. AMA

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EETIIQHE uvq u if 9/ fiw. 2 3 p W r. J 2" Q Q ATTORNEY Apnl' 7, 1953 D B. GARDINER 2,633,861

VALVE FOR POWER TRANSMISSIONS Filed June 28, 1945 2 SHEETS-SHEET 2 5g! 4 I o 54 i X-ll 3 INVENTOR. 33 DUNCAN B. GARDINER 'izwzzrw ATTORNEY Patented Apr. 7, 1953 VALVE FOR, POWER TRANSMISSIONS Duncan B. Gardiner, Detroit, Mich., assignor to Vickers Incorporated, Detroit, Mich, a corporation of Michigan Application. June 28, 1945, Serial No. 601,994

9 Claims. 1

This invention relates to valves for power transmissions, particularly to those of the type comprising two or more fluid pressure energy translating devices, one of which may function as a pump and another as a fluid motor.

The invention concerns flow-regulating valves used in such transmission systems for the purpose of regulating flow independently of pressure. Various types of flow-regulating valves are used in different systems, and heretofore each type of valve has been designed and constructed independently and differently from the others without regard to economies of manufacture which would ensue if all types were constructed from identical basic parts so far as possible.

In particular, the invention relates to an improvement in the construction of a valve body for housing the mechanisms comprising a simple flow-regulating valve, namely,

an adjustable throttle and a compensating valve, so that the same valve body may house an additional check valve or a pilot relief valve to form either a combined flow-regulating and check valve or a combined flow-regulating and overflow relief valve.

As disclosed in the patent to Vickers, No. 2,272,684, there is showna simple flow-regulating valve comprising a housing having an inlet and an outlet and containing an adjustable throttle and a compensating valve for maintaining a constant flow across the throttle through which fluid is adapted to flow at a regulated rate. The valve disclosed serves the purposeof controlling the speed of any liquidactuated member independently of the type of pump used or of load resistance.

In some cases where the speed of the liquidactuated member is to be controlled in one direction only with a rapid return in the other direction, a flow-regulating valve is used in combination with a check valve which may be integral or external, as disclosed in Figure 2 of the aforementioned patent to Vickers. The combination valve is used to pass the liquid through the compensating valve and throttle,

eliminate the need of a separate relief valve, the l special combination of an adjustable throttle, an overflow compensating, valve and a pilot relief valve, is used. As disclosed in this latter patent, the speed of the liquid-actuated member is not only controlled, but, in addition, the pump is only burdened with pressures slightly in excess of the existing load resistance, thus economizing on power consumption and giving longer life to the pump. I

In the past, when it was desirable to use a flow-regulating valve in combination with an internal check valve or to use the combined flow control and overflow relief valve, an entirely different body from that of the valve body housing the mechanisms of the simple flow control valve was employed. This necessitated an additional expense of providing special bodies for each type of valve with increased costs of manufacture due to the fact that market demands for each valve alone are much less than that for all types combined, and the cost of manufacture of each type was high because of production in smaller quantities. By providing a standard body for containing the mechanisms comprising a simple flow-regulating valve, which, by the provision of an auxiliary bore or other bores and a passage, may be used as a housing for containing the mechanisms comprising either a combined flow-regulating and check valve or a combined overflow and relief valve, the substantial savings created by manufacturing the one standard body in large quantities are made available. 1

It is an object of this invention to provide a valve body to house the mechanisms comprising a, simple flow-regulating valve, namely, an adju'stable throttle and a pressure-responsive compensating valve, which also may be used to house a check valve or a pilot relief valve in addition to thethrottle and compensating valve or overflow valve to form either a combined flow-regulating and check valve or a combined flowregulating and overflow relief valve.

It is also an object of this invention to provide a valve body for the purpose described and providing for simplification and economy in machining and assembly and for a fewer number of I parts.

It is also an object to provide an improved flow-regulating valve construction in which the parts are all more readily adapted to low-cost manufacture than previous valves for the same purpose and in which blind bores, multiple concentricities and other costly constructions are eliminated or reduced to a minimum.

Further objects and advantages of the present invention will be apparent from the following description, reference being had to the accompanying drawings wherein a preferred form of the present invention is clearly shown.

In the drawings:

Figure 1 is a diagrammatic view of a hydraulic circuit incorporating one form of the present invention and illustrating a sectional view taken on line II of Figure 2.

Figure 2 is a sectional view taken on line 2-2 of Figure 1.

Figure 3 is a front elevation of one form of the present invention.

Figure 4 is a diagrammatic view of a hydraulic circuit incorporating one form of the present invention and illustrating in cross-section a combined flow-regulating and overflow relief valve.

Figure 5 is a diagrammatic view of a hydraulic circuit incorporating one form of the present invention and illustrating in cross-section a combined flow-regulating and check valve.

Referring now to Figure 1, there is shown a pump I9, which may be driven by an electric motor, not shown, which is supplied with fluid from a tank I2 by means of a suction conduit I4 and which has a delivery conduit [6 connected to a pressure port I8 of a suitable four-way directional control valve 29. Incorporated in the pump delivery conduit I6 is a suitable relief valve 22 which has an exhaust conduit 24 connected to the tank I2 and which will limit the pressure in the system by relieving excessive fluid under pressure to tank I2.

The directional valve 29 is connected to a motor 26 having a piston 28 to which is connected a piston rod 39. A conduit 3| connects a cylinder port 92 of valve 29 to the head end of motor 26, and a conduit 33 connects another cylinder port 34 of valve 29 to the rod end of motor 26. A return conduit 36 connects a tank port 38 of the valve 29 with an inlet port 39 of a flow-regulating valve 49.

The flow-regulating valve 49 is comprised of a housing or body 42 having a main stepped bore 44 extending across the valve housing 42. A vertical passage 46 extends from the bottom of housing 42 and intersects bore 44. A passage 48, below bore 44, extends from the right side of housing 42 to a point where it intersects a passage 59 extending from the top of housing 42 and which is in communication with bore 44. A restricted passage 52 extends from the top of body 42 to a point of intersection with passage 48 and also into rear communicating with passages 48 and 59 at their point of intersection. A throttle 63, having a stepped bore 64 in which is threaded a plug member 65, all of which is more clearly shown in Figure 2, is inserted in bore 62.

Tightly inserted in bore 44 is a sleeve 66 having a shoulder 68 abutting a shoulder I9 of bore 44 which limits the extreme point of insertion of sleeve 66 in bore 44. Sleeve 66 has a groove 12 and a passage I4 in communication with passage 46, and a groove I6 and a passage I8 in communication with passage 59. Sleeve 66 also has a centrally-located longitudinal bore 89 in communication with the sleeve passages previously mentioned. A drilled passageway 82 ex tending the full length of the sleeve 66 is in communication with sleeve passage 18 but not with sleeve passage I4.

A compensating valve 84, comprising a piston 96 to which is connected a stem 88 provided with lands 99 and 92, is inserted in bore 44 of body 42 and bore 89 of sleeve 66, so that the left side of land 92 abuts a plug 94 threaded into bore 44. Piston 86 is hollow for the reception of one end of a spring 96 of predetermined resistance, the other end of which fits into a hollow plug 98 threaded into the right end of bore 44. A chamber in communication with passage 52 is formed in bore 44 between the right side of piston 86 and plug 98, and a chamber 91 in communication with passage 82 is also formed in bore 44 between the left side of piston 66 and sleeve 66. An inlet chamber 99 is formed in bore 89 of sleeve 66 between lands 9!] and 92.

As shown in Figure 2, bore 62 has a counterbore I99 forming a shoulder I9I, and a second counterbore I92 near the face of body 42 forms a shoulder I93. A combined knob and dial I94 has a bore I96 and a projecting portion I98. The left end of throttle 63 fits into bore I96, and a pin H9 is driven through a drilled hole H2 in portion I93 and a drilled hole H4 in throttle 63 to firmly connect dial I94 and throttle 63. When so connected, pin H9 which is longer in length than the diameter of portion I98 of dial I94, will have equally extended portions H9 on both top and bottom of the portion I98 on the right side of dial I94. A screw H9 is threaded through dial I94 into the left side of throttle 63.

Before throttle 63, which is connected to dial I94, is inserted in bore 62, a cover plate I29, containing a hole I22 of the same shape and approximate size as the portion I98 of dial I94 and having extended slots I24, all of which is shown in Figure 3, is screwed onto the face of body 42 so that hole I22 of plate I29 is in line with bore I99, and the extended slots I24 are in line with bore I92. It is a simple matter to then insert the throttle 63 to which is connected dial I94 so that a throttling slot I25 in the wall thereof is located in bore 62 with throttling slot I25 being in communication with passages 48 and 59 at their point of intersection. Plug 95 is provided with a suitable seal I21 to prevent leakage. The right end of throttle 63 is surrounded by a sleeve I29 threaded into the right end of bore 62 to form a recess for a sealing ring I 3|. Portion I98 of dial I94 fits through hole I22 of plate I29 into bore I99, with the portions H6 of pin H0 passing through extended slots I24 of hole I29 and resting on shoulder I93. By turning dial I94, the extended portions H6 of pin H9 are held between shoulder I93 and plate I29 so that dial I94 and throttle 63 are not only firmly connected and supported but easily rotated. Throttle 63, in which is inserted plug member 65, together with dial I94, when connected by pin H9 and screw H8, comprise a complete throttle and dial sub-assembly Body 42, containing compensating valve 84 and provided with the complete dial and throttle assembly I33, comprises a simple flow-regulating valve which may be incorporated in a hydraulic transmission to regulate the speed of a fluid motor regardless of load resistance.

Referring nowto Figure 1,, in operation, with the electric motor running and with piston. 28 of motor 26 in the position shown, if control valve 26 is shifted to connect conduit I6 to conduit 3| and conduit 33 to conduit 36, fluid under pressure from pump I6 is delivered through conduit I6 to pressure port I8 of valve 26 and by means of port 32 and conduit 3| to the head end of motor 26. As piston 26 shifts to the right, discharged fluid from the rod end of motor 26 is delivered by conduit 33, ports34 and 38 of valve 26 and conduit 36 to the inlet port 39 of valve 46. Fluid then enters inlet passage 56, groove 12, passage I4, inlet chamber 99, pass-age I8, groove I6, passag 56, across throttle 63, through throttling slot I25, and by means of passage 48, outlet passage 66, outlet port 56 and conduit 6| to tank I2.

Throttle 63 will have been Originally adjusted to pass a given quantity of fluid. Any amount delivered by pump I6 in excess of this quantity is always passed over relief valve 22. Compensating valve 84, which is responsive to the pressure drop across throttle 63, will maintain a constant flow across the throttle 63 in the well-known manner. Discharged fluid from motor 26 entering inlet chamber 99 and passage I8 also enters passage 82 in sleeve 66, entering chamber 91 to act on the left side of piston 86, and it also acts on the left side of land 92 by means of passage 82. Any increase or decrease of load resistance causing an increase or decrease of pressure will be reflected in chamber 91, and the resistance of I spring 96 will either be overcome by an increase to cause compensating valve 84 to shift to the right, or, in case of .a decrease in pressure, causing compensating valve 84 to shift to the left. Land 92 as a result either admits less fluid in case of an increase of pressure or admits more fluid in case of a decrease of pressure. As compensating valve 84 is immediately responsive to any pressure increase or decrease, it will maintain a constant flow across throttle 63. Any back pressure in conduit 6| will be compensated for also because this back pressure will be reflected in chamber 65 by means of passage 52.

If the directional movement of motor 26 is reversed by shifting valve 26, conduit I6 is connected to conduit 33,. and conduit 3| is connected to conduit 36. In this case, discharged fluid from the head end of motor 28 must first pass through flow-regulating valve 46 before going to tank I2, and the same regulation of discharged fluid takes place in the same manner. If the load resistance on motor 26 should suddenly change, any increase or decrease of resulting pressure is reflected in inlet chamber 9 9 so as to permit more or less fluid to enter so as to maintain constant the pressure in inlet chamber 99 and consequently maintain a constant flow across throttle 63. When thus connected in the transmission as shown in Figure 1, the speed of motor 26 is regulated in both directions.

If it becomes necessary to remove throttle 63 or compensating valve 84 for the purpose of inspection, maintenance or replacement, compensating valve 84 may be removed simply by taking out plug 98, and throttle 63 may be removed simply by turning dial I64 completely and lifting the complete dial and throttle assembly I33 from body42.

As shown in Figure 1, a simple flow-regulating valveis used in the discharge side of a hydraulic motor to utilize a well-known metering-out principle. In some cases more efficient results may i be obtained by placing a flow-regulating valve in ,6 the inlet sideof the transmission, and it may also be convenient to dispense with the necessity of installing a separate relief valve. In such a case, a basic body, such as shown in Figure 1 and which has already been described, may be utilized for this purpose. 7

Referring now to Figure 4, there is shown a hydraulic transmission such as is shown in Figure 1 but with relief valve 22 removed. Instead of having a simple'flow-regulating valve 46 in the discharge side of the motor, a combined flowregulating and overflow relief valve I26 is connected to the inlet side of the motor.

Valve I26 consists of a body 42' which contains the same bores and passages as body 42 of flowregulating valve 46. In addition, however, a bore forming an inlet passage I28 extends from the rear of body 42' to bore 44 in line with bore 44 at a point where passage 56 intersects bore 44. An enlarged bore of inlet passage I28 forms a pressure inlet port I36, also shown in dottedv lines in Figure 2. A vertical passage I35 extends from the bottom of body 42 to the chamber 95 and lies in a plane to the left of passages 46, 48 and 56, as shown in Figure 2. An auxiliary stepped bore I32 below passage 48 extends from the left side of body 42 to its point of intersection with vertical passage I35 and also intersects vertical passage 46-, as shown in Figure 2.

A compensating valve 64', essentially the same as compensating valve 84 of flow-regulating valve 46, is inserted in bore 44 and sleeve bore 86. Compensating valve 84' consists of a piston 86' connected to which is a stem 88' provided with lands 96' and 92'. Land 96' is slightly longer in length than land 96, and land 92 is slightly shorter in length than land 92 of compensating valve 84. When positioned in bore 44 of body 42' and bore 86 of sleeve 66 by plug 94, spring 96 and plug 98, land 96 permits communication between inlet passage I28 and passage 56 but blocks communication between sleeve passage I8 and an exhaust chamber 99'.

A pilot relief valve I34 is inserted in auxiliary bore I32. A sleeve I36 having a longitudinal bore I38, the extreme left end of which forms a seat I46 for a ball valve |42, is inserted in th right end of bore I32. Another sleeve I 44 having a longitudinal bore I46 is threaded over sleeve I36. Bore I46 forms an exhaust chamber I48 in communication with passage 46 by means of ports I56. A spring I52 of predetermined resistance located in chamber I48 has a retainer I54 at its right end which also holds ball valve I42 securely on the seat I46. Another spring retainer I56, which is shiftable within bore I46, abuts an adjusting screw I58 having a locking nut I66.

Pump delivery conduit I6 is connected to pressure inlet port I36, and an exhaust port 39 is connected by means of a conduit I62 to tank I2. An exhaust passage 56' connects to exhaust port 36 A pressure outlet port 58' is connected by means of a conduit I64 to. pressure port I8 of directional valve 26. The throttle and dial assembly I33 used in valve I26 i identical to that used in flow-regulating valve 46 both in construction and location, as is shown in Figures 2 and 3. When valve I26 is to be mounted against a flat surface, a sealing ring I65 (see Figure 2) will provide a leak-proof seal between valve I26 and the mounting surface.

In operation, with the electric motor running and pump I6 in operation, if valve 26 is shifted to connect conduit I64 to conduit 3| and conduit 33 to conduit 36.,fiuid under pressure from pump 7 I6 is delivered by means of delivery conduit I6 to the pressure inlet port I36 of valve I26 and by means of pressure inlet passage I28 and groove 76 in sleeve 66 to passage 58, across throttle 63, through passage 48 to pressure outlet passage 68', pressure outlet port 58' and conduit I64 to the pressure port I8 of valve 26 and by means of port 32 and conduit 3| to the head end of motor 26. Discharged fluid from the rod end of motor 26 enters conduit 33, ports 34 and 38 of valve 26 and is delivered by conduit 36 to tank I2.

Fluid from pump I6 entering inlet passage I28 of valve I26 is prevented from entering exhaust chamber 99' by reason of land 96' blocking communication between passage 78 and exhaust chamber 99'. Throttle 63 has been adjusted to pass a predetermined amount of fluid to which land 90' of compensating valve 84 offers no restriction, and the pump I I will only be burdened with pressures equal to load resistance on motor 26. Any tendency to increase or decrease the pressure is reflected in chamber 37 by means of passageway 82. Any increase or decrease in pressure beyond throttle 63 is reflected in chamber 95 by means of passage 52. If at any time the pressure drop across throttle 63 should exceed the resistance of spring 96, compensating valve 86' will shift to the right, and land 38' will open communication between passage 78 and exhaust chamber 99. Excessive fluid will be exhausted to tank I2 by means of passage 74, groove 72, passage 46, exhaust passage 56', exhaust port 39 and conduit I62. Only enough fluid will be exhausted to tank I2 to maintain constant the flow across throttle 63, and compensating valve 84 will maintain this flow constant by maintaining a constant pressure drop across throttle 63.

If at any time the pressure should reach a maximum point in the system as determined by the resistance of spring I52 of valve I34, this fluid pressure would unseat ball valve I42, and fluid from chamber 95 will exhaust through passage I35, stepped bore I32, seat I48, exhaust chamber I48, port I56, vertical passage 46, exhaust passage 56', exhaust port 39' and conduit I62 to tank I2. Due to the fact that fluid may be exhausted faster through pilot relief valve I36 than it can enter chamber 95 through restricted passage 52, the increased pressure in chamber 97 will shift compensating valve 84 to the right, and the entire pump volume will be exhausted to tank I2 by means of exhaust chamber 39, passage 74, groove 72, passage 46, passage 56', exhaust port 39' and conduit I 62. Thus, valve I26 not only serves as a fluid flow regulator but also performs the function of a relief valve.

If valve 20 is shifted to connect conduit I64 to conduit 33 and conduit 3| to conduit 38, the movement of piston 28 will be regulated in the same manner as the other described directional movement because fluid under pressure now being delivered to the rod end of motor 26 must also first pass through valve I26.

Flow-regulating valve 46 and flow-regulating and over-flow relief valve I26 have been shown and described as being able to regulate the speed of motor 26 in both directions although valve 46 was incorporated in the discharge side of the motor and valve I26 was incorporated in the inlet side of the motor. When it is desired to regulate the speed of motor 26 in one direction only with a more rapid return in the opposite direction, a combined flow-regulating and check valve I66, shown in Figure5, may be incorporated in the hydraulic transmission.

Valve I66 is comprised of a. body 42" identical to body 42 of flow-regulating valve 46 shown in Figure 1 with several additions. Passage I35 is drilled from the bottom of the body in the same plane as and intersecting with passage 48. An auxiliary stepped bore I68 is made in the left side of body 42" extending to vertical passage I35. and intersecting vertical passage 46. All other bores and passages are the same as contained in body 42 of valve 46. Likewise, the same sleeve 66, the same compensating valve 84 and throttle and dial assembly I33 used in flow-regulating valve 46 are utilized in the combined flow-- regulating and check valve I66. Located in stepped bore I68 is an insert I76 having a seat I72 for a hollow piston I74 which is shiftable within a sleeve I76 threaded into bore I68. A longitudinal bore I78 of sleeve I76 in which piston I74 is shiftable contains a light spring I79, one end of which abuts a plug I66 threaded into the left end of bore I68 and the other end of Which rests in piston I74 to normally position piston I74 lightly on seat I72. Piston I74 is provided with ports E82 in communication with ports I84 in sleeve I76 so that fluid in passage 46 tends to seat piston I74 while fluid in vertical passage I35 entering stepped bore I63 may unseat piston I74 and enter vertical passage 46 by means of seat 72 and port I84 of sleeve I76.

There is also shown a hydraulic transmission similar to that shown in Figure l, but, instead of having a flow-regulating valve 46 incorporated in the discharge side of motor 26 so as to regulate the speed of motor 26 in both directions, the combined flow-regulating and check valve is incorporated between the four-way valve and fluid motor so as to regulate the speed of motor 26 when fluid pressure is directed to the head end of motor 26 and to provide a rapid return when fluid pressure is directed to the rod end of motor 26.

Conduit I6 connects pump II] to port I8 of valve 26, and conduit 36 connects port 36 of valve 26 to tank I2. Conduit 33 connects the rod end of motor 26 to the inlet port 39 of valve I66, while a conduit 35 connects valve I66 to port 34 of valve 26. Conduit 3Iconnects port 32 of valve 26 to the head end of motor 26.

In operation, with the electric motor running and operating pump I6 and with valve 26 shifted to connect conduit I6 to conduit 3! and conduit 35 to conduit 36, pressure fluid from pump I6 is delivered by conduit I6 to port III of valve 20 and by port 32 and conduit 3I to the head end of motor 26. Discharged fluid from the rod end of motor 26 is delivered by conduit 33 to inlet port 39 of valve I66, and by means of inlet passage 56, vertical passage 46, groove 72 and passage 74 to inlet chamber 69.

Fluid leaves inlet chamber 89 by means of passage 78 and groove 76, enters passage 50, crosses throttle 63 and enters passage 48 and outlet pass'age 66 from where it is delivered to tank I2 by means of outlet port 56, conduit 35, ports 34 and 38 of valve 26 and conduit 36. Fluid entering vertical passage 46 is prevented from flowing from passage 46 to vertical passage I35 by piston I74. Compensating valve 84 and throttle 63 perform identically in the same manner as in valve 40 already described so as to regulate the speed of motor 26. However, when valve 26 is shifted to connect conduit I6 to conduit 35 and conduit 3| to conduit 36, compensating valve 84 mess-a1 and throttle 63 are bypassed in the following manner:

Fluid pressure from pump I is delivered by conduit I6 to port I8 of valve 20 and by means of port 34 andconduit 35 to the outlet port 58 of valve I66. Due to the 'fact that fluid flow will follow the line of least resistance, fluid entering outlet port58 will enter outletpassage 60, vertical passage I35, stepped bore I68, will unseat piston I14 and flow through seat I72, port I84, vertical passage 46, inlet passage '56, inlet port 33 and by means of conduit 33 to therod end of motor 30. Discharged fiuidfrom the head end of motor 26 is delivered by conduit 31, ports 32 and 38 of valve 20' and conduit 36 to tank I2. Due to the fact that compensating valve 8'4 and throttle 63 are bypassed, the full volume orpume I 0 is delivered to the rod end of mowers, and not a regulated amount less than full pump volume such as when fluid from I0 is directed to thehead end of instant. v g

It should be noted that the same dial and throttle assembly I33 may be utilized in valves 4|], I26 and I66, and that the same compensating valve 84 .is used in valves 40 and [66. e

It should also be noted that body 42 of valve 40 may be converted into a body 42' to contain the mechanisms comprising valve I26 simplyby adding a bore and counterbore to form pressure inlet port I30 and pressure inlet passage I2 8 respeotively, and also adding stepped bore I32 and vertical passage I35. 7

It should also be noted that body 42 of valve 40 may be converted into body 4 2" to contain the mechanisms comprising valve; I66 simply by adding auxiliary bores I35 and I68 and their associated vparts. V

It. should also be noted that compensating valve 84 or 84' and throttle and dial assembly I33 are easily removeddue to the construction of. basic body 42 and the construction of the throttle and dial'assembly I33.

While the form of embodiment of the invention as herein disclosed constitutesa preferred form, it is to be understood that other forms might be adopted; all coming within the" scope of the claims which" follow. i

What is claimed is a rouows;

i. For controlling new in hydraulic power transmission systems" a combined flew regulatin and check valve comprising in combination a basic; multiple purpose body member having a pressure compensating valve mounting bore, an

inlet and an outlet passage lo'catedhon the same side of the compensating valve bore and connected to the latter in spaced apart relationship and a throttle" receiving bore also on the same side of the compensating valve boreintersecting the outlet passage, an adjustable throttle through which fluid is adaptedtd flow at a regulated rate mounted in the throttle bore, a pressure compensating valve mounted in the compensating valve bor'e responsive to the pressure drop across the throttle for maintaining a regulated flow offluid throughthe latter, means-forming a stepped bore in said basic body intersecting the inlet and the outlet passage and a checkvalve mounted in said bore permitting free and unregulated fluid flow from the outletpassageto" the inlet passage.

2; For controlling flow in hydraulic power transmission systems a flow regulating valve of the excess dischargetype'comprising in combinationa basic multiplepurpose body member navinga pressure compensating valve mounting bore, a first and a second passage located on the same side of the compensating valve bore and connected to the latter in spaced apart relation ship and a throttle receiving bore also on the same side of the compensating valve bore inter seating the second passage, an adjustable throttle through which fluid is adapted to new at a regulated rate mounted in the throttle bore, an inlet passage formed in the basic bodym'ember perpendicular to the compensating valve bore and a pressure compensating valve or the normally closed type mounted in the compensating valve bore, responsive t'othe pressure drop acrossthe throttle forniaintaining a regulated now of fluid through the throttle. A

3 For entrpumg new in Hydraulic p wer transmission systems a 'cdnib'ined pressure limiting and flow regulating valve of the excess discharge type comprising in cdnibination a basic multiple purpose body member having a pressure compensating valve mounting bore, a first and a second passage located on the same side of the compensating valve bore and connected to' the latter in spaced apart relationship anda throttle receiving bore also on thesame side of the compensating valve bore intersecting the second passage, an adjustable throttle through which fluid is adapted new at a regulated rate mounted in the throttle bore,,an inlet passage formed in the basic body member perpendicular to the compensating valve bore, a pressure compensating valve of the normally closed type mounted in the compensating" valve bore, respon sive to the pressure dr-opacross the throttle for maintaining a regulated flow of fluid through the throttle, means forming an auxiliary passage in the basic body member intersecting the first passage and the compensating valve bore, and a pilot relief valve mounted in the auxiliary passage.

4. An improved flow regulating valve for controlling, flow in hydraulic power transmission systems comprising in combination a basic,- multiple purpose, body member having a pressure compensating valve-mounting bore, an inlet and an outlet passage located on the same side of the bore and connected thereto in spaced apart relationship, and athrottlerreceiving bore also on the sameside of the compensating valve mounting bore and intersecting the outlet passage, an adjustable throttlemounted in the throttle bore through which fluid is adaptedto flow at a regulated rate and a pressure compensating valve mounted in theic'ompensating valve bore responsive to the pressuredrop acrossthe throttle for maintaining the'regulated flow of fluid through the throttle.

5. A basic multipurpose body part for housingflow regulating valve mechanism of difierent types; said body havinga'longitudinal pressure compensating valve'bore; atransverse throttlere ceiving bore,- and two passages leading from the same surface of the body to the compensating valve bore, one of said passages intersecting the compensating valvebore at one point and theother passage intersecting the; compensating valve bore at two points-and also intersectingthe throttle bore; said-passages and throttle bore all being located inthe'body completely on one side of the compensating valve bore and said passages intersecting the compensatingvalve bore at predetermined spaced points so that pressure compensating valves of two di'iferent types may be mounted in the ccmpensaurig valve bore'without' altering the body, d'rie" typendrrnally permitting communication between the passages and" an one type of flow regulating valve and by constructing a third passage in the body to serve as an inlet flow passage leading to the compensating valve bore and mounting the other type of compensating valve in the body together with an adjustable throttle a flow regulating valve of another type is formed,

6. A basic multipurpose body part for housing an adjustable throttle and a pressure compensating valve of the normally open type to form a flow regulating valve of one type and for housing an adjustable throttle and a pressure compensating valve of the normally closed type to form a flow regulating valve of the excess discharge type, said body having a longitudinal pressure compensating valve mounting bore, a transverse adjustable throttle mounting bore and a pair of passages provided with fluid openings on one surface of the body, one of said passages intersecting the compensating valve bore and the other passage intersecting both the compensating valve bore and the adjustable throttle bore, said passages and transverse bore all being located on one side of the longitudinal bore, said passages intersecting the longitudinal bore in predetermined spaced apart relationship whereby upon mounting an adjustable throttle in the transverse bore and a pressure compensating valve in the longitudinal bore having lands of a dimension for normally permitting communication between the passages a flow regulating valve of one type is formed and whereby upon forming an additional flow passage in the body intersecting the longitudinal bore at a predetermined point and mounting an adjustable throttle in thetransverse bore and a pressure compensating valve in the longitudinal bore having lands of a dimension for normally closing communication between the original passages and permitting communication between the additional passage and one of the original passages, a flow regulating valve of the excess discharge type is formed.

7. A basic multipurpose body part for housing an adjustable throttle and pressure compensating valves of different types to form flow regulating valves of the simple one way type and of the excess discharge type, said body having a longitudinal bore and a transverse bore, said longitudinal bore being provided with three ports spaced along the bore in predetermined relationship, and a pair of passages with fluid openings on one surface of the body, one of said passages extending to one of the valve ports and the other passage extending to the other two ports and also intersecting the transverse bore, said transverse bore being formed for receiving an adjustable throttle and said longitudinal bore and valve ports being arranged for the receipt of a pressure compensating valve of a type for normally opening communication between two of said ports or for a pressure compensating valve of the type for normally closing communication between the same two ports, whereby said body part may be utilized to form a flow regulating of the one way type without alteration and may be utilized to form a flow regulating valve of the excess discharge type by the construction of an additional inlet flow passage leading from the same body surface as the other two passages and leading to one of the valve ports spaced along the longitudinal bore.

8. A basic multipurpose body part for housing flow regulating valve mechanism of different types, said body having a pressure compensating valve bore, a throttle receiving bore and two passages leading from the same surface of the body to the compensating valve bore, one of said passages intersecting the compensating valve bore at one point and the other passage intersecting the same bore at two points and also intersecting the throttle bore, said passages and throttle bore all being located in the body on one side of the compensating valve bore, said passages intersecting the compensating valve bore in predetermined spaced apart relationship so that pressure compensating valves of either the normally open or normally closed type may be mounted in the compensating valve bore without further alterations to the basic body, a flow regulating valve of the simple one way type being formed by mounting a throttle and a compensating valve of the normally open type in said body and a flow regulating valve of the excess discharge type being formed by constructing a third passage in the body leading from the same surface of the body as the other two passages and to the compensating valve bore at a predetermined point, and mounting a throttle and a pressure compensating valve of the normally closed type in the body.

9. A basic multipurpose body part for housing an adjustable throttle and a pressure compensating valve which may be of the normally open or normally closed type to form flow regulating valves of different types, said body having a 1ongitudinal bore provided with two valve ports and a valve controlling pressure port spaced in predetermined relationship along said bore, a pair of passages provided with fluid openings on the same surface of the body, one of said passages leading to one of the valve ports and the other passage leading to both the other ports, means forming a transverse bore intersecting the passage leading to the two valve bore ports, said passages and transverse bore all being located in the body completely on one side of the longitudinal bore, whereby an adjustable throttle and a pressure compensating valve of the normally open type may be respectively mounted in the transverse and longitudinal bores to form a simple one way flow regulating valve, and by constructing an auxiliary passage leading from the same surface of the body as the other passages and to the longitudinal bore at a point intersecting one of the valve ports, said body may be utilized without further alteration for mountmg respectively in the transverse and longitudinal bores an adjustable throttle and a pressure compensating valve of the normally closed type to form a flow regulating valve of the excess discharge type.

DUNCAN B. GARDINER.

REFERENCES CITED The followin references are of record in th file of this patent: 8

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